CN101779016A - Operation of internal combustion engine method and internal-combustion engine - Google Patents

Abstract

The invention describes a kind of operating method of internal-combustion engine, comprise at least one ram with the power house that is limited by power piston, described at least one ram has suction valve and outlet valve; At least one compression cylinder with the pressing chamber that is limited by compression piston, compression cylinder have fresh charge suction valve and flowing valve; And circulation chamber, described circulation chamber communicates with pressing chamber when flowing valve is opened, and communicates with power house when INO, said method comprising the steps of: when increasing compression chamber volume, make fresh charge flow into pressing chamber; When reducing compression chamber volume, compression is in the fresh charge in the pressing chamber; Push compressed fresh charge in circulation chamber; Fresh charge in the release circulation chamber is in power house; In the fresh charge in combustion powered chamber, the volume of power house increases, and simultaneously heat energy is converted into mechanical output kinetic energy, and when reducing the power house volume, discharges the charge after burning; Wherein, after having carried out at least a portion push-on process, the volume of circulation chamber increases, and the volume of circulation chamber is less than 15% of maximum volume when push finishes, and more excellent is less than 10%, and more excellent is less than 5%, and further more excellent is less than 1%.

Description

Operation of internal combustion engine method and internal-combustion engine

Technical field

The present invention relates to a kind of operation of internal combustion engine method and a kind of can be according to the internal-combustion engine of this kind method operation.

Background technique

For economizing on resources and reducing for the purpose of the environmental pollution, the development goal that urgency constantly promotes in the development of internal-combustion engine (particularly can be applied to the internal-combustion engine of passenger vehicle) reduces oil consumption exactly and/or raises the efficiency, mentioned herein to efficient can be understood as the mechanical energy efficient that oil consumption is brought into play with respect to bent axle.

The characteristic of conventional reciprocating internal-combustion piston engine be whole heat power process (air inlet, the compression, the burning and exhaust) result from the single cylinder, mean combustion fuel can utilize aspect have heavy losses.People have known the trial (trial shown in US 2005/0268609A1) that whole heat power process is assigned to two cylinders.In this well-known internal-combustion engine, the air inlet of fresh air is pushed to a ram by middle constant volume of interim connection from a compression cylinder.This propelling movement occurs under the situation that has the high pressure difference, because the cause of thermal loss and flow loss, efficient can not be satisfactory.

Another characteristic of modern stroke piston combustion engine is fuel injection techniques.Adopt this technology, gasoline or diesel oil are directly sprayed into the firing chamber.In the motor of spark ignition, though this technology does not require high fuel injection pressure, possess following each point: the control of point-device fuel injection point and fuel injection amount and pollution be reduced to bottom line and avoid the combustion-chamber geometry of the exhaust aftertreatment of costliness as far as possible according to combustion optimization theory design.In the operation of diesel engine, in order to lower smog, need very high fueling injection pressure (being higher than 2000 crust) and very expensive exhaust aftertreatment, comprise diesel particulate filter.

A kind of internal-combustion engine with regenerator and hot air ignition mechanism has been described in DE 60021901T2.A compression cylinder is connected with a ram by a regenerator.Have in the connector of a valve working between compression cylinder and regenerator.Regenerator is connected with exhaust by an outlet valve.

DE 3433619A1 has described a kind of have one first cylinder and one second cylinder and internal-combustion engine that the two links to each other by a circulation chamber each other.The connector of the chamber that circulates from first cylinder, be provided with a valve.The changeless circulation chamber of this volume is connected with second cylinder all the time.

DE 577740 has described a kind of charged air internal combustion engine, wherein has a circulation chamber R to be set between compression cylinder and the ram.The volume of above-mentioned circulation chamber is changeless.

US 1,771, and 335 have described a kind of internal-combustion engine, and this internal-combustion engine is according to a six-stroke periodic duty, and has a plurality of cylinders.Many intake manifold are formed in the cylinder cap of internal-combustion engine, manifold and two cylinder communications and liaison separately.In addition, also be provided with gas exhaust manifold, one in each cylinder.Being connected between air inlet and the gas exhaust manifold passage by a plurality of valves controls.In addition, also be provided with an auxiliary manifold in cylinder cap, this manifold is communicated with all cylinder, and they and being connected by a plurality of valves controls of each cylinder.

A kind of internal-combustion engine with a compression cylinder and a ram has been described in JP 57091324A.Described cylinder connects by circulation chamber, and compression piston and power piston the two be in top dead center simultaneously.Like this, the fresh momentum that is compressed by pressing chamber is all placed circulation chamber, and separates from ram.After the fresh momentum igniting in circulation chamber, the air-entry value that leads to ram is opened, and the fresh momentum of feasible burning expands and then enters ram.

The preamble of the application's independent claims is expressed by US 2007/0157894A1.This prospectus has been described an a kind of compression piston and internal-combustion engine that is operated in the power piston in the ram that is operated in the compression cylinder that has.A fresh charge suction valve is operated in the intake duct of pressing chamber.The pressing chamber of described compression cylinder links to each other with the power house of ram by a circulation chamber, is provided with a flowing valve just as one-way valve in its branch from pressing chamber.A suction valve is positioned in the circulation chamber opening that enters power house.Power house links to each other with the gas exhaust manifold of internal-combustion engine by an outlet valve.Described valve with by such as be formed in camshaft that bent axle links to each other on cam drive so that they are rotated simultaneously.Described bent axle links to each other with piston by piston rod.Power piston has 10 to spend to the advancement amount at 40 degree phase angles with respect to compression piston.The selection mode at phase angle described here is as follows: when compression piston when its top dead center moves, power piston is just in time removed from its top dead center, like this, the pressurized air of substantially the same quality is sent in the circulation chamber by power piston, and enters power house through circulation chamber.When power piston moves down further, common 10 spending in the scopes of 30 degree top dead center after, the air inlet that is positioned at power house is lighted a fire.During whole operation, just as the flowing valve and the suction valve that is positioned at power house of one-way valve gas pressure to be controlled at circulation chamber, the pressure value the when numerical value of this pressure is lighted a fire with air inlet at least is the same high.

Summary of the invention

The object of the present invention is to provide a kind of operating method and a kind of internal-combustion engine that increases with respect to the traditional combustion engine working efficiency of internal-combustion engine.

Claim 1 has been stated a kind of method that reaches the object of the invention.

Be positioned at the fresh air of the pressing chamber of heat power cylinder outside by compression, simultaneously by (this fresh charge all is compressed in each operation cycle with fresh charge, and in each operation cycle, be pushed into circulation chamber according to demand by when compressing further) major part at least almost be pushed to fully even in the power house and these air be used for burning, make compression work be minimized, filling effect is improved simultaneously, the efficient of internal-combustion engine and then be improved.

The preferred embodiment that dependent claims 2 to 22 is intended to state method of the present invention.

Claim 23 has been stated a kind of internal-combustion engine that is intended to reach about invention part purpose.

Internal-combustion engine of the present invention is further improved by the optimal way that technical characteristics constituted in the middle of the claim 23-43.

By means of method of the present invention and/or internal-combustion engine of the present invention, all basically combustion gas and liquid fuel are all by perfect combustion.For example, importing the combustion gas of pressing chamber upstream or combustion gas and the liquid fuel in liquid fuel or the importing pressing chamber all can utilize fresh air being treated as the good ignition mixture of a kind of spy between compression period in compression cylinder and in the process of chamber of next flowing through and circulate.This mixture is then just released power house in the high pressure mode from circulation chamber, burns under the situation without any spark ignition around here simultaneously.Like this, diesel fuel just can be used under the situation that needn't adopt the high pressure oiling, and gasoline can be used under the situation of spark ignition not having.Around here owing to adopted very good mixing thing preparation process, and then obtained oligosaprobic exhaust.

To in conjunction with complementary schematic representation and more detailed data the present invention be narrated with the form of giving an example below, the present invention is applicable to the internal-combustion engine of stationary applica-tions and the internal-combustion engine on the traffic tool such as automobile and boats and ships.

Description of drawings

Fig. 1 is the generalized section with internal-combustion engine of compression cylinder, circulation cylinder and ram of the present invention.

Fig. 2 to Fig. 8 is that internal-combustion engine among Fig. 1 is at the view of different operating during the stage.

Fig. 9 has shown the volume-variation of bent axle when diverse location.

Figure 10 has shown the variation and the valve open-close number of times of bent axle pressure when diverse location.

Figure 11 is the stereogram of an exemplary valve mechanism.

Figure 12 is the sectional drawing that is provided with the circulation piston of flowing valve.

Figure 13 is the stereogram of the suction valve that is provided with in opposite mode.

Figure 14 is the stereogram that is used to drive the roller cam follower of circulation piston.

Figure 15 has shown an embodiment of the valve mechanism that has adopted Figure 13 and part shown in Figure 14.

Figure 16 is the schematic representation with internal-combustion engine of intake manifold fuel injection of the present invention.

Figure 17 is the schematic top plan view of multi-cylinder engine of the present invention.

Figure 18 is the schematic perspective view of the demonstration bent axle of the piston in the piston-cylinder unit of internal-combustion engine shown in Figure 13.

Embodiment

According to Fig. 1, internal-combustion engine of the present invention comprises a bent axle 10, and bent axle 10 has two adjacent cranks, and one of them crank links to each other with compression piston 16 by piston rod 12, and another crank links to each other with power piston 18 by piston rod 14.Compression piston 16 can move in compression cylinder 20.Power piston 18 can move in ram 22, and ram 22 preferably studs with cylinder sleeve 24.

These preferably be formed on cylinder in the common cylinder shell 28 by cylinder cap 30 from top seal, this cylinder cap comprises the thin end wall 32 that is formed on two cylinders 20 and 22 zones that overlap; This end wall 32 from top seal the part of cylinder 20 and cylinder 22, and sealed the circulation cylinder 33 that is formed in the cylinder cap 30 from the bottom.

Pressing chamber 34 is formed between compression piston 16 and the cylinder cap 30 (as shown in Figure 3).Power house 36 is formed between power piston 18 and the cylinder cap 30; Fuelinjection nozzle 38 extend in the power house 36.

Circulation piston 40 can move in circulation cylinder 33; Circulation piston 40 defines circulation chamber 42.

The intake manifold 44 of fresh air and/or fresh charge is formed on the cylinder cap 30; Fresh charge suction valve 46 moves and controls the connection between fresh charge intake manifold 44 and the pressing chamber 34 in intake manifold 44.Fresh charge comprises pure fresh air and is mixed with the fresh air of fuel and/or remaining exhaust.

Gas exhaust manifold 48 also is formed on the cylinder cap 30; Outlet valve 50 moves and controls being communicated with between power house 36 and the gas exhaust manifold 48 in gas exhaust manifold 48.

The communication port that connects pressing chamber 34 and circulation chamber 42 is formed on the end wall 32; Flowing valve 52 moves in communication port and opens in the mode away from pressing chamber.The axle of flowing valve 52 is directed motion in the mode of sealing in circulation piston 40, the active force that flowing valve 52 can withstand spring 53 enters into circulation piston 40 inside, can stretch out circulation piston 40 again in limited stroke.

Move in suction valve 54 another opening on end wall 32, this opening connects circulation chamber 42 and power house 36; The axle of the suction valve 54 also mode of sealing is directed motion in circulation piston 40.

Fresh charge cam 56, exhaust cam 58 and intake cam 60 are used for driving respectively valve 46,50 and 54.

These cams are formed on one or more camshafts in a kind of appropriate mode, and this camshaft is preferably driven with the rotational speed identical with bent axle by bent axle 10.

The function of internal-combustion engine provided by the invention according to its basic structure, will describe by Fig. 2 to Fig. 8.For clearer explanation, will in above-mentioned accompanying drawing, insert several corresponding numbers.

Fig. 2 has shown that the compression piston 16 of internal-combustion engine of the present invention has reached its top dead center, the stage the when volume of pressing chamber is in minimum (almost nil).Circulation piston 40 is in position near its top dead center (position when the top dead center position of circulation piston 40 is meant the volume minimum (almost nil) of circulation chamber 42).Power piston 18 has left its top dead center.In this embodiment, power piston 18 has the advancement amount of some degree with respect to compression piston 16, and this advancement amount is realized by the suitable deviator of the associated crank of bent axle 10.

At this moment, fresh charge suction valve 46 cuts out, and flowing valve 52 is closed, and suction valve 54 is opened, and outlet valve 50 is closed.

Stage shown in Figure 2 is roughly corresponding to the next stage, that is, fresh charge begin to be inhaled into and/or pressing chamber 34 in begin to inject fresh charge, and the compressed fresh charge that is contained in circulation chamber 42 does not also flow in the power house 36 fully.

Fig. 3 has shown the stage that the fresh charge injection in the pressing chamber 34 has been finished substantially.At this moment, compression piston 16 almost is in its lower dead center; Circulation piston 40 is in its top dead center, and just the volume of circulation chamber is position hour; Power piston 18 is in the terminal point of power stroke, and this power stroke stage and then shown in Figure 2 takes place, and in this stage, fresh charge is burned.Fresh charge suction valve 46 still is in open mode, and the active force that flowing valve 52 overcomes spring 53 enters into the inside of circulation piston 40, and suction valve 54 and outlet valve 40 are in closed condition.

In the stage shown in Figure 4, the compression of fresh charge begins, and meanwhile, the exhaust after the burning begins to discharge.Compression piston 16 begins to move upward from its lower dead center, the fresh charge in the compression pressing chamber 34.Circulation piston 40 still is in the position of its top dead center.

At this moment, flowing valve 52 and suction valve 54 are closed, and power piston 18 begins to move upward, and outlet valve 50 is opened.

In the stage shown in Figure 5, compressed charge begins to flow into circulation chamber 42 in pressing chamber 34.

When fresh charge suction valve 46 still cut out, compression piston 16 beginnings were near its top dead center.Circulation piston 40 leaves its top dead center, and flowing valve 52 shifts out in flowing valve piston 40 under the effect of spring 53, and opens under the pressure effect in pressing chamber 34.Thereby compressed fresh charge can flow into circulation chamber 42, and at this moment, suction valve 54 is in closed condition.Meanwhile, power piston 18 also almost arrives its top dead center, and at this moment, outlet valve 50 still is in opening state at the terminal point of expansion stroke.

Fig. 6 has shown the working stage that shows than Fig. 5 internal combustion engine stage of 1 a little later.In this stage, compression piston 16 reaches its top dead center, and at this moment, fresh charge suction valve 46 further cuts out, and power piston 18 also reaches its top dead center fully.At this moment, along with circulation piston 40 also almost moves to its lower dead center, flowing valve 52 is opened fully.Because the effect of circulation piston 40 inner spring power, make the flowing valve 52 can be too away from circulation piston 40, therefore, when circulation piston 40 moved to its lower dead center, flowing valve 52 can rise from its valve seat, thereby guaranteed the unlatching of flowing valve 52.Thereby the fresh charge that is compressed piston 16 compressions flow in the circulation chamber 42.

When compression piston reached its top dead center, it is minimum that the volume of pressing chamber 34 reaches, this minimum volume preferably pressing chamber 34 require to bear to greatest extent within.

In the stage shown in Figure 7, the compression piston 16 of internal-combustion engine still is in the position of its top dead center, and power piston 18 has begun to leave its top dead center position.

At this moment, fresh charge suction valve 46 is in closed condition.Along with of the top dead center motion of circulation piston 40 towards it, the volume reducing of circulation chamber 42, owing to lack the pressure effect in the pressing chamber 34, flowing valve 52 is closed, suction valve 54 is opened, compressed fresh charge in the circulation chamber 42 is injected in the power house 36, because power piston 18 in motion down, makes the volume of power house 36 increase.At this moment, outlet valve 50 is closed.

Fig. 8 showed than stage of 1 a little later in stage shown in Figure 7, in this stage, circulation piston 40 reaches its top dead center, this moment, flowing valve 52 was closed, suction valve 54 cuts out once more, and whole compression charge all enters into power house 36, because this moment, outlet valve 50 was still closed, the self ignition of the diesel oil by injecting power house 36 a little earlier, the charges in the power house 36 take fire.In the embodiment of toroidal swirl type spark-ignition internal combustion engine, the fuel injection ratio stage shown in Figure 8 but almost lights a fire the stage shown in Figure 8 a little earlier.In the embodiment of non-toroidal swirl type spark-ignition internal combustion engine, the mixing of fresh charge and fuel occurs in before the fresh charge suction valve 46, perhaps occurs in the circulation chamber 42.

It is minimum that the volume of circulation chamber 42 reaches at the top dead center place of circulation chamber, and this minimum volume does not preferably surpass the necessary limit that circulation chamber 42 can bear.This minimum volume should more preferably be less than 10% less than 15% of circulation chamber maximum volume (circulation piston be positioned at lower dead center), more preferably is less than 5%, further more preferably is less than 1%.

Stage shown in Figure 8 be assumed that than internal-combustion engine the residing stage of Fig. 2 a little later so that finish whole circulation.

Compressed fresh charge in circulation chamber 42 is injected into power house 36 incipient stage in (Fig. 6 is to the stage shown in Figure 7), control to suction valve 54 and outlet valve 50, be in the time of to guarantee that circulation chamber 42 began with being communicated with of power house 36 preferably and/or will finish the time, the pressure difference of these two chambers is less than 15 crust, more excellent is less than 10 crust, and more excellent is less than 5 crust.And the structure of valve is unrestricted.Preferably, when circulation chamber 42 and power house 36 was communicated with, two chambers had pressure much at one.Outlet valve 50 will be closed before power piston 18 arrives top dead center, so that the part residual gas can be stayed in the power house 36.When outlet valve 50 was closed, suction valve 54 preferably still was in closed condition; And when the pressure difference between power house 36 and circulation chamber 42 reaches above-mentioned pressure difference, perhaps when the pressure of two chambers is roughly the same, suction valve 54 is just opened, so that fresh charge can be pushed into power house 36 from narrow and small circulation chamber 42 in the mode of a kind of energy and/or heating power optimization.

As mentioned before, fresh abrim in compression cylinder 20, especially cold charge under full load situation and compressed charge.Along with the increase of the volume of circulation chamber 42, the compression charge is pushed into circulation chamber; Then, along with reducing of circulation chamber volume, the compression charge is pushed out into power house from circulation chamber; Then, mechanical motion is finished in the charge burning in the power house.Pressurized air in the pressing chamber 34 is pushed in the circulation chamber 42, is pushed out into the power house 36 from circulation chamber 42 again, and whole process all is to finish in a kind of energy-optimised mode under the condition that only has insignificant pressure difference between the chamber that respectively communicates.

Because heating power, for the maximization of implementation efficiency, pressing chamber 34 should be cold as much as possible, and power house 36 should be warm as much as possible.Therefore, compression cylinder 20 should be heat insulation with ram 22 as much as possible, and obtain cooling as much as possible.And ram is only guaranteeing that material is unlikely to just to be cooled under the overheated situation.Above-mentioned purpose can be by the cooling manifold that does not show among the reasonable distribution figure, and/or between pressing chamber cooling system and power house cooling system, other cooling system is set and realizes, also can realize by insulation bushing is set in compression cylinder and/or ram.The power piston 18 of motion preferably is designed to help heat insulation hierarchy in heat power chamber 36, perhaps covers the thermal-protective coating that one deck such as pottery is made.

Because when the fresh charge of compression was pushed into power house, charge exchanged, therefore only need ram is cooled off a little.By integrated design to flowing valve 52 and circulation piston 40, can conserve space, and flowing valve can have a big flow cross.

For adiabatic, circulation piston 40 preferably is designed to adiabatic in its side in the face of end wall 32, for example adopt independent heat insulation layer.Ram also preferred design becomes adiabatic, for example adopts embedded lining.Preferably, the top of power piston 18, and the bottom of the cylinder cap 30 relative with power piston top comprise that at least the appropriate section of end wall 32 is all carried out insulation.

In the above embodiment of the present invention, the operation of power piston 18 is in advance in compression piston 16, that is to say that power piston 18 is than compressing the top dead center that piston 16 reaches it more earlier, this high pressure fresh charge that can cause releasing power house from circulation chamber can't further be compressed by the power piston.In order to realize high pressure gentle high pressure eventually, power piston preferably postpones a little with respect to compression piston, can further be compressed by the power piston to such an extent as to release the fresh charge of power house from circulation chamber, at this moment, the extra compression of wall heat that these fresh charges also can be absorbed by power house.This also reduces the cooling requirement of power house.

With reference to Fig. 9 and Figure 10 the corresponding embodiment of internal-combustion engine of the present invention is described below.Fig. 9 has shown the volume-variation that changes the power house 36, pressing chamber 34 and the circulation chamber 42 that cause along with crank position.Wherein, the top dead center of power piston (minimum volume of power house 36) is defined as 0 degree.Figure 10 provides the change in location along with bent axle, the variation in pressure in power house and the pressing chamber and the open-close time point distribution situation of related valve.

As shown in the figure, when being about-150 ° in crankangle, fresh charge suction valve 44 cuts out, promptly after compression piston has just arrived its lower dead center.Along with the volume of pressing chamber 34 reduces, the pressure of pressing chamber (dash curve) increases.When crankangle was about-100 °, the circulation piston began to leave its top dead center, and the volume of circulation chamber 42 begins to increase.When angle was about-95 °, flowing valve 52 was opened, and along with the volume of pressing chamber 34 further reduces further to increase with the volume of circulation chamber 42, compressed fresh charge is pushed in the circulation chamber 42.When angle was about-75 °, outlet valve 50 was closed, and the discharge of the charge in the power house 36 after the burning finishes.When angle is about-65 °, for example reach the position of maximum volume about circulation chamber 42, suction valve 54 is opened, pressurized air is released from circulation chamber in the power house, at this moment, the pressure of circulation chamber pressure best and power house is roughly the same, and perhaps pressure difference is less than 15 crust, be more preferably less than 10 crust, or even less than 5 crust.Compressed-air actuated pushing with push proceeded, and reaches their minimum volume up to pressing chamber and circulation chamber; At this moment, pressure also rises thereupon, reaches about-20 ° up to angle, and at this moment, compression piston and circulation piston all reach top dead center, and flowing valve 52 and suction valve 54 all are in closed condition.

Compression charge in the power house is lighted, and the variation in pressure in the power house 36 as shown in figure 10.When crankangle was about 10 °, fresh charge suction valve 44 was opened, and the intake process of pressing chamber 34 begins once more.When crankangle was about 140 °, outlet valve 50 was opened, and the charge after the burning is discharged.

According to above-mentioned process control because power house 36 has lasting high wall temperature and the high temperature residual gas that sprays into, even under the help that does not have spark plug, the gasoline that is directly injected to power house also can burn, this point is similar from ignition procedures to diesel oil.Therefore, method of the present invention both had been suitable for gasoline and also had been suitable for diesel oil.

From above as can be known, compressed fresh charge flow into circulation chamber 42 in compression cylinder 22, and this fresh charge be pushed into the process of power house from circulation chamber can be by multiple diverse ways control.From the fluid angle, if compressed fresh charge is pushed into the circulation chamber that begins to enlarge in its compression process in pressing chamber 34, when between circulation chamber and power house, having formed pressure balance at least haply, be pushed out and enter into power house from circulation chamber again, and, can in the process that the compression charge is released, be kept in this pressure balance roughly between circulation chamber and the power house, so just can be reached the optimization of energy.Therefore, push with push and can overlap.If the volume of pressing chamber is zero when push-on process finishes, the volume of circulation chamber also is zero when push finishes, and can be sure of that then compressed fresh charge has all entered into power house outside power house.If push-on process just begins after the process of circulation finishes, at this moment, the pressure of circulation chamber can increase because of the energy of exhaust, because the energy of exhaust can heat the fresh charge that is temporarily stored in the circulation chamber; And push occurred in the shorter time period, and then such design is favourable for the burning situation in the power house.

From above can further finding out, the compression ratio of fresh charge is by the ratio decision of the maximum volume and the volume (being the minimum volume of power house 36) after the compression of pressing chamber.Expansion ratio by power house 36 when outlet valve 50 is opened volume and the ratio decision between the volume after the compression, so expansion ratio is greater than compression ratio.Internal-combustion engine of the present invention can move the expansion stroke of expansion, for example big expansion ratio than compression ratio, thus realize better thermal performance.

The actual compression ratio of fresh charge, the ratio between the volume of the fresh charge that just each intake stroke sucks and the minimum volume of power house can regularly change by the control of fresh charge suction valve 46.According to the application's the field and the loading spectrum of motor, only operation expansion expansion stroke is suitable in the load operation scope of a part, promptly bigger than compression ratio expansion ratio.This can regularly realize by the valve control that changes fresh charge suction valve 46, for example more a period of time of morning is closed fresh charge suction valve 46 by before arriving top dead center at compression piston, perhaps in the low load of internal-combustion engine, after arriving top dead center, compression piston closes fresh charge suction valve 46, so that the volume of the fresh charge after actual suction and the compression reduces.In this case, it is suitable making compression piston 16 and compression cylinder 20 have the physical dimension identical with power piston 18 and ram 22, for example, has identical piston external diameter and stroke of piston.Equally, the compression chamber volume when compression piston arrives top dead center is preferably 0, and compressed fresh charge all is pushed in the circulation chamber.

Figure 11 is the schematic representation of the cam mechanism of one embodiment of the invention.The part 70 of ram end wall surrounds power house 36 from the top.The part 72 of compression cylinder end wall surrounds pressing chamber 34 from the top.The label of valve and cam is consistent with accompanying drawing before.

Valve system comprises two camshafts 74 and 76; Be installed in a gear 78 on the axle, link to each other with crankshaft gear by chain or cam band, and with the speed rotation identical with bent axle.Above-mentioned camshaft is installed in the bearing that does not show in the drawings, so that they are fixed with respect to internal-combustion engine, above-mentioned camshaft also comprises pitch wheel 80 and 82, so that they rotate in the opposite direction with identical speed.Also be provided with two fresh charge suction valves 46 on this valve mechanism, the fresh charge cam 56 that each fresh charge suction valve 46 is separately positioned on camshaft 74 and 76 drives.

As shown in the figure, outlet valve 50 is set at the exhaust cam (not shown) driving on camshaft 74 or 76.Certainly, outlet valve 50 also can be set at two cam drive on the camshaft, and two outlet valves perhaps also can be set.

The intake cam 60 that suction valve 54 is set on the camshaft 74 drives, and wherein the axle of suction valve passes circulation piston 40 in the mode of sealing, and is high-visible from Fig. 1.Circulation piston 40 is seen as ellipse from plan view, and it overlaps with the part of pressing chamber 34 and power house 36 respectively, and four axles to that indicated in the drawings are one-body molded.Be provided with circulation cam 62 on each camshaft 74 and 76, it is all inconsistent with the cam 62 that circulates to be installed on the free-ended roller 84 of axle.

Roller 84 is inconsistent with circulation cam 62 under the elastic pressure of spring 86, this spring 86 is supported between the axle (not marking among the figure) of internal-combustion engine casing and circulation piston 40, in other words, this spring upwards acts on the circulation piston 40 among Fig. 1, it is in makes circulation chamber 42 have the position of maximum volume.Cam 62 has such external frame: when they when the cam base circle, circulation piston 40 overcomes spring force and is pressed towards the volume that makes circulation chamber 42 downwards and reaches minimum and/or almost nil position; And, the external frame of cam 62 be designed to make the circulation piston finish with Fig. 9 in the corresponding stroke of two point dashed trace, at this moment, the variation in pressure in the circulation chamber has made full use of the spring force of spring 86.Above-mentioned structure has been arranged, and the same with existing cam drive mechanism, cam mechanism does not need to bear high surface pressure.

Figure 12 has shown the sectional view of the circulation 40 with suction valve 54 and flowing valve 52.When circulation piston 40 is encapsulated on the cylinder cap 30 (as shown in Figure 1), it can move up and down by one or more Sealings 90.The axle of suction valve 54 is by a sleeve pipe 92 guiding, and the sealing between maintenance and the sleeve pipe 92; And sleeve pipe 92 is guided by circulation piston 40, and the sealing between maintenance and the circulation piston 40.

The axle of flowing valve 52 can be directed certain deviator of moving under the condition that guarantees sealing in circulation piston 40, and bears the downward active force (as shown in figure 12) of spring 94.The upper end of spring 94 links to each other with a joint of circulation piston, and its lower end links to each other with a joint on being fixed on flowing valve 52.Sleeve pipe 96 is installed in the upper end of the axle of flowing valve 52, comprise one can be with respect to the lining of circulation piston 40 motion h distances, this h distance is more much smaller than 40 maximum stroke of circulation piston.

On illustrated position, suppose that circulation piston 10 makes circulation chamber 42 be in minimum volume, the valve block of flowing valve 52 contacts on the valve seat 58 that is formed on the end wall 32 (as shown in Figure 1).

As mentioned before, run to the process of distance for this section stroke of h at the top dead center of circulation piston 40 from it, flowing valve 52 is to be in initial closed condition always, and when circulation piston 40 continued to move upward, flowing valve 52 was pulled away from valve seat 98.Size design according to spring 94, before circulation piston 40 is finished the stroke of h distance, pressure in the pressing chamber 34 just is enough to overcome the spring force of spring 94, therefore leaves its top dead center when circulation piston 40 1, and flowing valve 52 just is opened under the pressure effect of pressing chamber 34.

Internal-combustion engine embodiment of the present invention also can have following various deformation:

Flowing valve 52 also can be designed to the form of simple safety check, and this safety check overcomes the acting force of the spring on the internal-combustion engine casing under only the pressure in pressing chamber 34 promotes and opens, and wherein, this spring force can be regulated as required.

By with suitable manner structure circulation piston, be that the flowing valve of independent parts also can be omitted.

Circulation piston 40 also can be pushed into fresh charge power house 36, and horse back was to its lower dead center motion after suction valve 54 cut out, can increase the volume of circulation chamber 42 like this, so that compression piston 16 is injected into fresh charge in the circulation chamber 42 immediately after beginning to move upward.

For the open-close time point with each valve applies in the working environment, phase regulator need be set.And, might not can rotation by the I. C. engine crankshaft (not shown) directly drive valve, but, come valve is carried out appropriate control by the valve driver of each valve oneself is set.Actual compression ratio and ignition condition can be put by the shut-in time of outlet valve and control; If desired, this shut-in time point also can be applicable to different running environment by suitable controlling device.

For heatable catalytic formula exhaust purifier when starting and in the process of heating, it is reasonable adopting variable valve system to drive valve 50, can make opening with rapid heatable catalytic formula exhaust purifier of morning of valve 50 like this.Same, also can come heatable catalytic formula exhaust purifier by control flowing valve 52, be injected into power house and/or make late as far as possible the carrying out of compression process so that fresh charge is later.

In order to make the charge motion in the power house 36 more accurate, be preferably a covering appts is set on suction valve 54.

Except cam mechanism, also can adopt hydrodynamic(al), pneumatic or power-actuated mode to drive circulation piston 40, especially accurately drive the occasion of circulation piston 40 at needs.

The motion of circulation piston also can be controlled like this, promptly when the compression stroke of compression piston begins, and the position that the circulation piston is the volume that almost is positioned at circulation chamber when maximum at least.Then, flowing valve is in open mode in the whole compression stroke of compression piston, and the compression process of fresh charge and process that fresh charge pushes circulation chamber are taken place synchronously, perhaps is to overlap to take place at least.

According to specific Structure of Internal-Combustion Engine and characteristic, compression cylinder and/or ram preferably are equipped with a system that can regularly change geometrical compression ratio or actual compression ratio by the control of appropriate change valve.Same, compression cylinder and/or ram preferably also can be equipped with such system, and it is poor that this system can change the motion phase of compression piston and power piston associated therewith.

Because the power that frequently replaces can act on chain or the cam band, for example therefore the gear 78 (as shown in figure 11) of drive cam shaft preferably is provided with a jack shaft between bent axle and camshaft; In Figure 11, this jack shaft preferably is arranged on the below of camshaft 74 and 76, so that save the size of cylinder cap on short transverse.This jack shaft comprises a undersized actuation gear, so that this jack shaft can be to be higher than the speed rotation of camshaft.Two camshafts preferably can be driven in the opposite direction by the gear on the jack shaft, and wherein, the gear of two camshafts will be accordingly more greatly, so that realize between bent axle and the camshaft 1: 1 velocity ratio.In order to compensate single order mass moment loss (in being provided with of 4 cylinders, having 2 compression cylinders/ram unit), except the compensation quality on bent axle, preferably on camshaft, also dispose compensation quality with the direction rotation opposite with bent axle; For example, compensation quality is configured in two ends of camshaft and is offset 180 ° mutually.

The size of piston can design according to different requirements with stroke of piston, and these design proposals can be considered some heating power factors, for example, as how low intensive compression and circulation work to realize high-intensity as far as possible power house 36 air inlet work; Do not have at internal-combustion engine under the situation of external spark igniting, just need make fresh charge when power piston 18 reaches top dead center position, reach specified temp, to guarantee no matter be that the fuel of direct injection or the gas of directly introducing can both produce reliable spontaneous ignition.For the external spark firing mode of using gasoline, the temperature that compression ends can be corresponding lower.

Internal-combustion engine of the present invention can be used as airbreathing motor or supercharged engine is used.

Also can control charge composition in the ram (being similar to the two stroke IC engine that has by the valve of cylinder cap control) by an extra bleed valve is set, that is to say, this bleed valve can assist to scavenge, thereby when " exhaust valve closure ", in the ram more fresh air is arranged, and reduced temperature.

Internal-combustion engine embodiment shown in Fig. 9,10,11 and 12 has following parameter:

	Compression piston	The circulation piston	Power piston
				External diameter (mm)	??86	??65*	??115
Stroke (mm)	??86	??7	??120
				Volume (cm when being positioned at top dead center 3)	??～0	??～0	??38

^*In the present embodiment, the circulation piston is oval-shaped, so that the best requirement of satisfying volume-variation and flow cross variation.

The overexpansion rate of this internal-combustion engine is about 2.5, can realize best full load efficiency.Less overexpansion rate as 1.8, is preferably for the efficient of optimizing in the fractional load scope, and in other words, power piston can be designed to littler.

According to internal-combustion engine of the present invention, direct injection diesel oil and gasoline can be realized surpassing the actual intermediate pressure of 20 crust and surpass 55% practical efficiency.

When corresponding piston during at top dead center separately, power house is reasonable to the V/V of circulation chamber between 25 to 60.When corresponding piston during in lower dead center separately, pressing chamber should be between 15 to 25 to the V/V of circulation chamber.The geometrical compression ratio of power house is reasonable between 25 to 40.When flowing valve arrived its top dead center, suction valve normally cut out, preferably, this suction valve before power piston arrives top dead center, crankangle also is in closed condition when being between 20 to 5 °.Above-mentioned parameter only is exemplary, is not limited in this.

In non-external spark ignition operation, a kind of glow plug can also be installed and improve the cold-starting ability.

What internal-combustion engine recited above adopted is ram 22 to be carried out direct fuel spray (Fuelinjection nozzle 38), and internal-combustion engine described here also can utilize any liquid or gaseous fuel to work under the situation that does not have the external spark igniting basically.

In foregoing, the time point of direct fuel injection is not described in detail, reason is, known to everybody, the time course of direct fuel injection is selectable, and said here fuel sprays and can be subdivided into pre-spray (this fuel sprays and occurs in before the top dead center of power piston) and main injection (this fuel sprays in the zone that occurs in this top dead center or after this top dead center).According to the present invention, fuel can be sprayed into (liquid fuel) power house or can be that is to say that fuel can be sprayed into power house when having only residual gas in the power house by (Figure 10) introducing (gaseous fuel) power house between time point B and C.Described residual gas is compressed simultaneously together with the fuel that sprays into, therebetween owing to occurred homogenizing fully between the cause fuel of high temperature and the residual gas, make fuel at time point C, the time point of inlet open just, present gas form completely (even adopted be that the diesel oil situation also is like this), and fully burn by the fresh air of spontaneous ignition with compression.The quantity of residual gas is determined by the shut-in time point B of outlet valve in the power house.Opening time of suction valve point C puts D with the shut-in time of suction valve and converts fired state to together with the volume of pressing chamber, circulation chamber and power house and the volume that is in the power house of power piston top dead center, burns so that air-fuel-residual gas mixture is gone up substantially after the power piston top dead center.The selection of time period makes that homogenizing of fuel-residual gas mixture that the front is introduced is able to appear at before the compression fresh air is introduced in a kind of sufficient mode between time point B (exhaust valve closure) and the time point C (inlet open).Directly spray into fuel and to compare near the power piston top dead center, fuel of the present invention sprays into and/or residual gas is introduced the advantage that not only has the aspect of homogenizing, also have this simultaneously and spray into the advantage that occurs in lower pressure level, this has just reduced the spending that fuel sprays into the equipment aspect.In view of spraying into the power house that comprises fresh air according to traditional approach fuel, according to the present invention, the fresh air after the compression is fed in the power house that a inside presents non-combustible fuel-residual gas mixture.

Particularly all the more so when internal-combustion engine is worked together together with the external mix thing formation system of power house outside.Will talk about as following, from circulation chamber 42 release fresh momentum to the push of power house 26 must be adjusted to power house 36 combustion process adapt so that make pressure in the circulation chamber 42 be higher than pressure in the power house 36.When the quantity of the fresh air that sprays in each power cycle (quantitatively control) increased along with load rise, the pressure in the circulation chamber 42 increased.On the other hand, when suction valve 54 was opened, the pressure that is present in the power house 36 changed with the change of load hardly.Therefore, as shown in figure 13, be necessary suction valve 54 to be set in opposite mode.

As shown in figure 13, suction valve 54 pressurizes downwards from the top by means of the spring of itself, is close proximity to the valve seat that is arranged in the inboard wall of cylinder cover 32 (Fig. 1), that is to say that the valve disc of suction valve 54 is formed with the seat surface that comes to a point gradually downwards.The unlatching of suction valve 54 is reached by a roller rocking arm 102.This roller rocking arm is supported between the roller bearing of the connected member of the roller rocking arm 102 that has spring 100 and roller rocking arm.Described roller rocking arm is positioned on the cam 60, and cam holds on 104 at the rotary-inversion axis that is fixed on the internal-combustion engine housing.Preferably, rotary-inversion axis holds 104 and is formed as a valve-lash-adjusting element.As shown in the figure, roller rocking arm 102 turns round along the power that counterclockwise overcomes spring 100 under the effect of intake cam 60, so that open this valve during by the indoor opened by pressure of power at suction valve 54.

Described valve seat is preferably in and forms a residual gas separation layer on the wall of power house.

As the explanation of having done by means of Figure 11,, need employ many power and drive the circulation piston for fresh momentum being released and being made it enter power house.In order to apply these power under the situation of not bearing excessive load at valve mechanism, preferably utilize one or (if required) a plurality of roller cam followers 106 as shown in Figure 14.Roller cam follower 106 is arranged on the housing of internal-combustion engine, can adopt a valve-lash-adjusting element at 108 places if necessary.Deviate from the end of bearing 108 at it, a roller 110 of roller cam follower contacts at circulation cam 62.Between the bearing 108 on roller 110 and the roller cam follower 106, inserted a cam follower 112; Described cam follower 112 drives circulation piston 40 (as Fig. 1).By adopting the lever of this structure, the stroke that cam follower 112 is finished can be shortened with respect to the stroke of roller 110, and the power that is transferred on the circulation piston by cam follower 110 can correspondingly increase.

Figure 15 shows the valve mechanism with Figure 13 and 14 structural elements, and its structure is because of adopting the auxiliary and clear expression of drawing reference numeral, so also just explain no longer in detail.Can use individually according to the structure shown in Figure 13 and 14, also can merge application.

Below can also utilize external mix thing formation system to operate by Figure 16 explanation internal-combustion engine.

Figure 16 shows a schematic diagram that comprises the unit of compression cylinder 20, circulation cylinder 33 and ram 22.A Fuelinjection nozzle 106 is arranged in the fresh momentum intake manifold 44 of compression cylinder 20; As everyone knows, in traditional intake manifold fuel injection system, Fuelinjection nozzle is injected to liquid fuel or inflammable gas in the fresh momentum intake manifold 44; Described fresh momentum intake manifold 44 is introduced fresh air by an air filter, and perhaps the compressor with an air inlet system links to each other.Particularly for multi-cylinder engine, situation is all the more so when one or more Fuelinjection nozzles 126 are set at every fresh momentum intake manifold 44 of leading to compression cylinder 20, this moment, the fuel injection preferably was not to carry out continuously, but only in certain time period, just pressing chamber 34 just carries out the fuel injection by the time period of fresh momentum suction valve 46 (not illustrating) the filling fresh air of unlatching in Figure 18.

The liquid of any kind or gaseous fuel can spray into by Fuelinjection nozzle 126.Non-volatile diesel fuel also can spray into, condition is that the mixture that is generated will be vaporized basically fully in the compression process of pressing chamber 34 at least, and next will be by circulation chamber 42 with its propelling movement and make it enter power house 36, also to carry out pretreatment in the best way and homogenize.Mixture be pushed out and send into power house that part of since be present in this power house high wall temperature and since by be present in power house in hot residual gas fully mix and reach ignition condition.So, no matter be diesel oil air mixture or benzine-air mixture (when adopting gasoline work), perhaps gas-air mixture (when adopting combustion gas work) spontaneous ignition is not finished quickly, but as shown in Figure 10, it is a kind of burning relatively stably, reason is that it is a time course that mixture is released, the appearance of its pressure process is unlike the situation that pulse operation occurred of traditional petrol engine or traditional diesel engine, do not rely on that external fuel sprays and direct fuel injection to the such pressure peak of power house.As the result of this smooth combustion, the size of the member of bearing load can be dwindled widely, and can be prolonged widely the working life of internal-combustion engine.Adopt another advantage that this method of the present invention had to be to save the exhaust aftertreatment that particulate filter and traditional cheap catalyzer of utilization carry out and just can satisfy the strictest exhaust emissions laws and regulations requirement, particularly spray into and the describing love affairs condition is all the more so with regard to the intake manifold fuel of diesel oil.For some particular job condition (for example cold-starting or lower part load), providing a kind of in power house also is desirable such as spark plug or the such igniting aid of glow plug.

Still the external fuel injection is irrelevant in power house with direct fuel injection basically for moment of torsion that described internal-combustion engine had and power characteristic, and wherein the system pressures (the upstream fuel pressure of Fuelinjection nozzle) of 3 to 8 crust are enough to satisfy the requirement that external fuel sprays.

Fuelinjection nozzle 126 or other Fuelinjection nozzle might not need to be arranged on the upstream of pressing chamber 34.Fuel can also directly spray in pressing chamber 34, also can directly spray in circulation chamber 42.

The huge efficient that the present invention brought improves at least owing to one of following factor:

The part of compression appears at outside firing chamber and/or the power house, and therefore this compression also just appears at lower temperature, and compression work is minimized.The energy of part exhaust obtains utilizing by being injected in the red-hot firing chamber and/or also absorbing heat energy in the red-hot power house there through the fresh momentum (having passed through heating significantly or heating by a small margin) of overcompression.In order to utilize heat of exhaust better, can use the exhaust of flowing out from gas exhaust manifold 48, by be introduced into rear side such as circulation piston 40, along or pass the rear side of above-mentioned piston and/or heat circulation chamber 42 by the annular wall that adds type of thermal communication cylinder 33.In this case, the circulation piston is not heat-insulating for circulation chamber.This kind situation also is suitable for for two circulation cylinders, and at this moment the circulation chamber of this cylinder alternately obtains the fresh momentum of exhaust and compression.The heating of circulation chamber can be considered to be in to be carried out under the situation that does not improve the pressing chamber temperature as far as possible.When heating was pushed into the compressed fresh momentum of circulation chamber, this fresh momentum was by hot compression further, and the opening time of suction valve point also matches with it.

The thermal loss of wall portion is lowered, because only require slightly with respect to the heat-insulating power house of compressor and to cool off, we can say that also power house can fully abandon external refrigeration.

Process steps is along with the expansion of expansion is carried out.

Internal-combustion engine additional advantage of the present invention is operating steadily of it and it compatibility to various different fuels.Its operation can be adopted liquid fuel, gaseous fuel and powdered solid fuel.

Figure 17 shows the schematic diagram of a kind of three-port type internal-combustion engine of the present invention, and wherein those piston-cylinder units that introduce separately, that be made of compression cylinder 20, circulation cylinder 33 and ram 22 are configured to a continuous row.Compression piston 16 and power piston 18 can be connected in shared bent axle 124 by piston rod 120,122 (Figure 18), show the axis of this bent axle among Figure 17 with two-dot chain line.The compression piston 16 of each unit and piston rod 120 and power piston 18 and piston rod 122 can be worked together by shared crank, and this crank comprises one to have two and separate toward each other and along the crank pin of the crank pin section that vertically distributes successively of bent axle 124; Phase deviation between desired power piston 18 and compression piston 16 motions obtains because of adopting described crank pin section.Power piston 18 also can be worked with they self pairing skew and/or crank with compression piston 16, so that obtain the expection phase deviation between power piston and the compression piston.Certainly, this side-play amount also can be zero.

For all valves and circulation piston provide a cam mechanism, for example according to Figure 11 or 15, this cam mechanism extends along entire internal combustion engine.

Piston-cylinder unit with compression piston, circulation piston and power piston of the present invention can be provided with any amount and arrangement, as the known setting of traditional combustion engine.

In order to reduce the warpage of internal-combustion engine, particularly for embodiment with two compression cylinders and two rams, preferably ram is set to the outer distolateral of internal-combustion engine, just is positioned at that side of control mechanism and that side of flywheel, and compression cylinder is set between two rams.But,, can be arranged at compression cylinder distolateral and ram is set between two compression cylinders in order to optimize balance and to shorten the lay length of the gas handling system conduit that may adopt.

Internal-combustion engine of the present invention can operated according to the air-fuel mixture (λ=1) that chemical equivalent calculates aspect direct fuel injection and the injection of intake manifold fuel, also can operate according to the relevant fuel injection amount of pure load.Under first kind of situation, the quantity of air must be controlled and be measured according to the relevant mode of load, makes fuel injection amount be converted to the flow rate of air.According to the operation point of internal-combustion engine, might become another kind of operator scheme from a kind of mode transitions.Pairing operator scheme has been determined to be used for the employed catalyzer of exhaust aftertreatment and has been used for required other important parameters such as exhaust gas recirculation quantity of exhaust aftertreatment in a kind of known mode.

Internal-combustion engine of the present invention is the internal-combustion engine that pluralities of fuel all is suitable for, and that is to say that this internal-combustion engine can utilize all types of basically liquids and gases fuel works as described like that.Pairingly can be determined in known manner, and single valve control timing can utilize corresponding Valve Drive System to convert pairing fuel to by fuel that use up and/or initiate.Particularly, can also influence the temperature that power house is reached by opening time point and the change circulation piston that changes outlet valve with respect to the motion phase that bent axle rotates when power piston is in the time point of top dead center.

In order to improve the low-temperature startup performance that intake manifold fuel sprays, it is desirable that a heating element that is used for interim heating is set on the Fuelinjection nozzle opposite.Can improve the formation of mixture under cold state by this heating element.Also have, an interim heating element (for example glow plug) is set in power house also is good.

Particularly all the more so when adopting straight spray mode to work.Can accomplish to use identical valve control regularly to operate the internal-combustion engine that adopts different fuel, only need to adopt automatically controlled Fuelinjection nozzle can reach above-mentioned requirements at an easy rate by changing the type that the fuel injection adapts to fuel opportunity.

Described straight spray method or be such with the method that fuel is introduced ram, be that fuel is introduced in the compressed gas that comprises fresh air, or fuel is introduced in the residual gas that does not comprise any air and/or any oxygen, or fuel is introduced from the ram upstream uncompressed or the compressed fresh air, aforesaid way can merge each other, so that utilize diverse ways to draw various fuel ratios.Described fuel ratio can change, and for example adopts load mode relevant or temperature correlation to change.

For internal-combustion engine of the present invention, the following possibility that is used for load control and fuel introducing exists:

Under environmental conditions or under the low barotropic state of gaseous fuel or under low barotropic state with the liquid fuel of gasoline or diesel oil form, can realize fuel is sprayed into intake manifold, for example realized by a multiple spot fuel injection system.For this purpose, can adopt " lambda 1 " (lambda 1) controller or lean-burn controller, perhaps adopt quantitative control, or adopt by means of the quantitative control that can control the fresh momentum suction valve that regularly changes with respect to valve by means of the throttle valve in the intake manifold.Also have, liquid fuel can directly be injected in the compression cylinder, can also directly spray into if desired in the circulation cylinder.Load this moment can be controlled by means of throttle valve, perhaps is better to have variable valve control fresh momentum suction valve regularly by means of one to control with " lambda 1 " controller and a lean-burn controller.Load can also the based on fuel amount be set.

In another case, gasoline or diesel oil can directly be sprayed onto in the red-hot ram, and load can be adjusted by the fuel quantity that sprays into.

In the process of fuel being introduced in the intake manifold or being introduced in the pressing chamber, be preferably the control that this mode of flow rate of controlling fresh air by the Variable Valve Timing of utilizing fresh momentum suction valve realizes load.Power house to the volume ratio of pressing chamber can for, for example, between 1 and 3.Wherein, the ratio of the internal-combustion engine that is used for the passenger traffic means of transportation when being used for truck is low, and be the highest with the ratio that is used for fixing the formula internal-combustion engine, because the latter is with operation at full load most of times.

The content of the residual gas in power house can be controlled by means of the Variable Valve Timing of outlet valve, wherein, when mainly with operation at full load, can adopt fixing the setting valve timing of outlet valve.

Phase difference between power piston and compression piston can be, for example ,-5 ° and+crankangle between 10 °, wherein Re power piston preferably has certain delay with respect to cold compression piston.

In the embodiment described above, preferably, fresh momentum suction valve is opened after the top dead center of compression piston, for example within 20 ° after the top dead center of compression piston; And after the lower dead center of compression piston, close, for example within 20 ° after the lower dead center of compression piston.

Flowing valve is preferably in to be opened before the compression piston top dead center fully, for example before the top dead center of this compression piston 90 ° open, and be preferably in the top dead center scope of compression piston and close.

Preferably, the suction valve that connects circulation chamber and power house was opened before the top dead center of power piston, for example before the top dead center of this power piston 10 °.And after the top dead center of the power piston of heat, close for example after this power piston top dead center 35 °.The firing duration that wherein is pushed out into the fresh momentum of power house is crossed over the process of the whole unlatching of suction valve basically.

Preferably, outlet valve ground far away after the top dead center of the power piston of heat is opened just now, and for example after the top dead center of this power piston 150 °, and close before being preferably in the top dead center of power piston, for example before the top dead center of this power piston 70 °.

Preferably, circulation piston local setting in motion far away before the top dead center of compression piston, for example before the top dead center of this compression piston 90 °.The circulation piston is preferably in stop motion after the top dead center of cold compression piston, for example after the top dead center of compression piston 30 °.

The parameter of more than enumerating only is the character of giving an example, and also nonrestrictive, is applicable to such as situations such as external mix thing formation.

Reference list

10 bent axles

12 piston rods

14 piston rods

16 compression pistons

18 power pistons

20 compression cylinders

22 power cylinders

24 cylinder sleeves

28 cylinder shells

30 cylinder caps

32 end walls

33 circulation cylinders

34 pressing chambers

36 power houses

38 Fuelinjection nozzles

40 circulation pistons

42 circulation chambers

44 fresh charge intake manifold

46 fresh charge suction valves

48 gas exhaust manifolds

50 outlet valves

52 flowing valves

53 springs

54 suction valves

56 fresh charge cams

58 exhaust cams

60 intake cams

62 circulation cams

70 end walls

72 end walls

74 camshafts

76 camshafts

78 gears

80 gears

82 gears

84 rollers

86 springs

90 Sealings

92 sleeve pipes

94 springs

96 sleeve pipes

98 valve seats

100 springs

102 roller rocking arms

104 rotary-inversion axis hold

106 roller cam followers

108 bearings

110 rollers

112 cam followers

120 piston rods

122 piston rods

124 bent axles

126 Fuelinjection nozzles

Claims (43)

1. the operation of internal combustion engine method comprises

Have at least one ram of power house, described power house is limited by power piston, and described at least one ram also has suction valve and outlet valve,

Limited by compression piston at least one compression cylinder with pressing chamber, described pressing chamber, described compression cylinder also has fresh charge suction valve and flowing valve, and

Circulation chamber, described circulation chamber communicates with described pressing chamber when described flowing valve is opened, and communicates with described power house when described INO, said method comprising the steps of:

-when increasing described compression chamber volume, make fresh charge flow into described pressing chamber,

-when reducing described compression chamber volume, compression is in the fresh charge in the described pressing chamber,

-push described compressed fresh charge in described circulation chamber,

-release described fresh charge in the described circulation chamber in described power house,

-in the described fresh charge of burning in the described power house, the volume of described power house is increased, simultaneously heat energy is converted into mechanical output kinetic energy, and

-when reducing described power house volume, discharge the charge after the described burning,

It is characterized in that:

When having carried out the described push-on process of at least a portion, the volume of described circulation chamber increases, and when described push finishes, the volume of described circulation chamber is less than 15% of its maximum volume, more preferably being less than 10%, more preferably is less than 5%, further more preferably is less than 1%.

2. method according to claim 1 is characterized in that, is in the almost whole compressed fresh charges in the described circulation chamber after described push-on process finishes, and is pushed out in the described power house in described push.

3. method according to claim 1 and 2 is characterized in that the volume of described circulation chamber changes corresponding to the motion of described compression piston and/or described power piston.

4. according to any described method of claim 1 to 3, it is characterized in that, when in described circulation chamber and the described power house roughly pressure balance exists the time, the push that is in the described compressed fresh charge in the described circulation chamber begins.

5. according to any described method of claim 1 to 4, it is characterized in that under the situation of no remarkable hypotension, described compressed fresh air is released in the described ram (22) from described circulation cylinder (33).

6. according to any described method of claim 1 to 5, it is characterized in that described outlet valve was closed before described power piston arrives top dead center.

7. according to any described method of claim 1 to 6, it is characterized in that, push described compressed fresh charge and overlap in time to the described push-on process of described pressing chamber (42) and the push of releasing described compressed fresh charge from described circulation chamber.

8. according to any described method of claim 1 to 6, it is characterized in that, push described compressed fresh air and do not overlap in time to the described push-on process of described pressing chamber (42) and the push of releasing described compressed fresh charge from described circulation chamber.

9. according to any described method of claim 1 to 8, it is characterized in that when described push-on process finished, the volume of described pressing chamber was almost nil.

10. according to any described method of claim 1 to 9, it is characterized in that the motion of described power piston is with respect to the motion delay of described compression piston.

11., it is characterized in that in the upstream of described circulation chamber, fuel is added in the described fresh charge according to any described method of claim 1 to 10.

12. method according to claim 11 is characterized in that, described fuel is gasoline, diesel oil or gaseous fuel.

13., it is characterized in that described fuel is joined in the described fresh charge stage by stage according to claim 11 or 12 described methods.

14. according to claim 11 or 13 described methods, it is characterized in that, release described fresh charge and overlap to the push of power house and the combustion process of the fresh charge in the described power house.

15., it is characterized in that according to any described method of claim 11 to 14, be pushed to the fresh charge of described power house, owing to the wall temperature of described power house and with mixing fully of hot residual gas reach autoignition conditions in the described power house.

16., it is characterized in that fuel is introduced directly in the described power house (36) according to any described method of claim 1 to 10.

17. method according to claim 16 is characterized in that, after the charge of fuel after described burning discharged and described compressed fresh charge be added in the described power house (36) before being pushed out into described power house.

18., it is characterized in that according to claim 16 or 17 described methods, from described circulation chamber (42), be pushed out into the described compressed fresh air of described power house (36), before taking fire, further compressed by described power piston (18).

19., it is characterized in that described circulation cylinder (33) is heated by the exhaust of described internal-combustion engine according to any described method of claim 1 to 18.

20. according to any described method of claim 1 to 19, it is characterized in that the geometrical compression ratio that described fresh air is experienced moves to geometrical compression ratio that top dead center this process experienced from being introduced into described ram (22) to the piston (18) that runs on the described ram greater than described fresh air outside described ram (22).

21., it is characterized in that described compression cylinder (2) is cooled so that disperse at least a portion heat that produces in the process of the described fresh air of compression according to any described method of claim 1 to 20.

22. according to any described method of claim 1 to 21, it is characterized in that the volume of the volume of the fresh charge that each aspirating stroke flowed into described power house when the ratio of the volume of described power house is opened less than described outlet valve during stop to described power piston is to the described power piston ratio of described power house volume during stop thereon thereon.

23. internal-combustion engine comprises

Have at least one ram (22) of power house (36), described power house (36) is limited by power piston (18), and described at least one ram (22) also has suction valve (54) and outlet valve (50),

Have at least one compression cylinder (20) of pressing chamber (34), described pressing chamber (34) is limited by compression piston (16), and described at least one compression cylinder (20) also has fresh charge suction valve (46) and flowing valve (52),

Circulation chamber (42), described circulation chamber communicate with described fresh air chamber when described flowing valve is opened, when described INO, communicate with described power house,

Crank mechanism (10), described crank mechanism are connected in described power piston, described compression piston and control gear (53,56,58,60,62) to control the operation of described each valve, make:

-when increasing described compression chamber volume, fresh charge flows into described pressing chamber,

-when reducing described compression chamber volume, the fresh charge that is in the described pressing chamber is compressed,

-compressed fresh charge is pushed in the described circulation chamber,

Compressed fresh charge in the-described circulation chamber is pushed out in the described power house,

-in the fresh charge of burning in the described power house, the volume of described power house increases, and simultaneously heat energy is converted into mechanical output kinetic energy, and

-when reducing described power house volume, discharge the charge after burning,

It is characterized in that:

Described circulation chamber (42) is limited by the circulation piston (40) that moves between stop and the lower dead center thereon, wherein, the volume of described circulation chamber when described circulation piston is in top dead center is less than 15% of the volume of described circulation chamber when described circulation piston is in lower dead center, more preferably be less than 10%, more preferably be less than 5%, further more preferably be less than 1%, and the motion of described circulation piston match with the motion of described compression piston (16) and/or power piston (18).

24. internal-combustion engine according to claim 23 is characterized in that, the external diameter of described compression piston (16) and stroke are all less than the external diameter and the stroke of described power piston (18).

25., it is characterized in that described pressing chamber (34) is almost nil at the volume of compression piston (16) when being in top dead center according to claim 23 or 24 described internal-combustion engines.

26., it is characterized in that described circulation chamber (42) is almost nil at the volume of circulation piston (40) when being in top dead center according to any described internal-combustion engine of claim 23 to 25.

27., it is characterized in that described compression piston (16) and described power piston (18) are connected in common bent axle (10) according to any described internal-combustion engine of claim 23 to 26.

28., it is characterized in that described at least fresh charge suction valve (46), described suction valve (54) and described outlet valve (50) are driven by a cam mechanism that is driven by crank mechanism (10) according to any described internal-combustion engine of claim 23 to 27.

29., it is characterized in that described circulation piston (40) is driven by a cam mechanism (74,76) that is driven by described crank mechanism (10) according to any described internal-combustion engine of claim 23 to 28.

30. internal-combustion engine according to claim 29 is characterized in that, described cam mechanism (74,76) comprises a plurality of cams (62) that drive described circulation piston (40).

31. according to any described internal-combustion engine of claim 23 to 30, it is characterized in that, described compression cylinder (20) and the adjacent setting of described ram (22), and described circulation piston (40) is operation in circulation cylinder (33), from described piston (16,18) moving direction, described circulation cylinder (33) overlaps mutually with described compression cylinder and described ram and is limited by end wall (32), and described end wall (32) is also shared by described compression cylinder and described ram institute; Also being formed with on the described end wall (32) can be by described flowing valve (52) and the mobile opening of described suction valve (54).

32. internal-combustion engine according to claim 31 is characterized in that, the axle of described suction valve (54) passes described circulation piston (40) in the mode of sealing.

33. internal-combustion engine according to claim 32 is characterized in that, described suction valve (54) is a mushroom valve, and the valve disc of described mushroom valve is in the described circulation chamber (42), closes described suction valve (54) when it is mobile towards described end wall (32).

34. according to claim 32 or 33 described internal-combustion engines, it is characterized in that, described flowing valve (52) is a mushroom valve, and when it is opened when the direction away from described pressing chamber (34) moves, and the axle of described flowing valve is directed in described circulation piston (40) in the mode of sealing.

35. internal-combustion engine according to claim 34, it is characterized in that, when described circulation piston (40) was in its top dead center, described flowing valve (52) was closed, and described flowing valve (52) can overcome the spring force that is arranged at the spring (53) in the described circulation piston and shifts out described circulation piston.

36., it is characterized in that described ram (22) and described compression cylinder (20) are adiabatic mutually, and the temperature of described ram is higher than the temperature of described compression cylinder according to any described internal-combustion engine of claim 23 to 35.

37. according to any described internal-combustion engine of claim 23 to 36, it is characterized in that, described internal-combustion engine also comprises a plurality of piston-cylinder units that are arranged in a row, and each described piston-cylinder unit comprises compression cylinder (20), ram (22) and circulation cylinder (33), wherein, described compression cylinder and described ram are separately positioned on one among adjacent two rows and arrange, and described compression piston and described power piston are connected in common bent axle, and described circulation piston (40) is by at least one common camshaft actuated.

38. according to any described internal-combustion engine of claim 23 to 37, it is characterized in that, comprise that the fuel supply device of Fuelinjection nozzle (106) is arranged on the upstream of described fresh charge suction valve (46).

39., it is characterized in that described fuel supply device comprises the heating equipment of the injected liquid fuel that is used to vaporize according to the described internal-combustion engine of claim 38.

40., it is characterized in that according to any described internal-combustion engine of claim 23 to 39, also comprise a fuel supply device, described fuel supply device comprises that a burner oil arrives the Fuelinjection nozzle (38) in the described power house (36).

41., it is characterized in that described fuel supply device sprays diesel oil, gasoline or gaseous fuel according to any described internal-combustion engine of claim 23 to 40.

42. according to any described internal-combustion engine of claim 37 to 41, it is characterized in that, also comprise the device that an induction installation and that is used to respond to fuel type is used to change described valve phase place and opens the endurance, described device can be according to the fuel type that uses, and changes the phase place of described valve and opens the endurance and/or change the motion of described circulation piston (40) with respect to described crankshaft rotating.

43. according to any described internal-combustion engine of claim 23 to 42, it is characterized in that, also comprise the induction installation that is used to respond to the induction installation of air-fuel ratio and is used to respond to described internal-combustion engine rotational speed, comprise a device in addition, this device can change the phase place of described valve and opens the endurance and/or change the motion of described circulation piston (40) with respect to described crankshaft rotating according to described air-fuel ratio and described rotational speed.

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